JP2011208569A - Temperature difference power generation device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a temperature difference power generation device attaining high power generation efficiency.SOLUTION: The temperature difference power generation device 1A includes: a compressor 31 compressing heat pump working fluid; a superheater 32 provided between an evaporator 12 and a turbine 13A, superheating power generation working fluid by exchanging heat between the heat pump working fluid compressed by the compressor 31 and the power generation working fluid evaporated by the evaporator 12, and discharging the same to the turbine 13A; an expansion valve 33 expanding the heat pump working fluid discharged from the superheater 32; and a heat recovery implement 34 heating the heat pump working fluid by exchanging heat between the heat pump working fluid discharged from the expansion valve 33 and heat source fluid discharged from the evaporator 32, and discharging the same to the compressor 31.

Description

  The present invention relates to a temperature difference power generation apparatus using a theoretical cycle of an external combustion engine such as Rankine cycle, Carina cycle, Uehara cycle and the like.

As a measure against global warming, reduction of carbon dioxide emissions and the importance of energy saving are increasing recently.Temperature difference power generation using geothermal water pumped from the ground and hot wastewater discharged from various factories as a heat source, Temperature difference power generation using a temperature difference between a relatively high temperature hot seawater in the ocean surface and a relatively low temperature cold seawater in the deep ocean has been performed.
Patent Document 1 describes a temperature difference power generation apparatus using a so-called carina cycle in which the thermal efficiency of a Rankine cycle, which is a kind of theoretical cycle of an external combustion engine, is improved. Patent Document 2 describes a temperature difference power generation apparatus using a so-called Uehara cycle, which further improves the thermal efficiency of the carina cycle.

Japanese Unexamined Patent Publication No. 57-200607 Japanese Patent Laid-Open No. 7-91361

  These conventional temperature difference power generation devices vaporize the power generation working fluid by exchanging heat between the fluid supplied from the heat source and the power generation working fluid in the evaporator, and the vaporized power generation working fluid drives the turbine to generate power. However, the temperature, pressure, and enthalpy of the power generation working fluid discharged from the evaporator and supplied to the turbine are determined by the temperature of the fluid supplied from the heat source. For example, when the temperature of the fluid supplied from the heat source is a medium to low temperature of 25 to 200 ° C., the enthalpy of the power generation working fluid supplied to the turbine is small and the heat drop before and after driving the turbine is small. Efficiency will be low.

  The present invention has been made in view of the above-described problems, and an object of the present invention is to provide a temperature difference power generation device capable of realizing high power generation efficiency.

  In order to solve the above problems, a temperature difference power generation device according to the present invention includes an evaporator that vaporizes the power generation working fluid by exchanging heat between the heat source fluid supplied from the heat source and the power generation working fluid, and the evaporator. A pump for supplying the power generation working fluid; a turbine driven by the power generation working fluid vaporized by the evaporator; a generator for generating power by driving the turbine; and condensing the power generation working fluid discharged from the turbine And a condenser that discharges to the pump, and is provided between the evaporator that compresses the heat pump working fluid, the evaporator, and the turbine, and is compressed by the compressor. In addition, heat exchange between the heat pump working fluid and the power generation working fluid vaporized by the evaporator causes the power generation working fluid to be overheated and discharged to the turbine. Heat exchange between a superheater, an expansion valve that expands the heat pump working fluid discharged from the superheater, and the heat source fluid discharged from the evaporator and the heat pump working fluid discharged from the expansion valve And a heat recovery unit that heats the heat pump working fluid and discharges it to the compressor.

  According to such a configuration, the heat that could not be given to the power generation working fluid by the evaporator is recovered to the heat pump working fluid by the heat recovery unit and is given to the power generation working fluid by the superheater. The power generation efficiency can be increased.

  The temperature difference power generation device is provided between the pump and the evaporator, and exchanges heat between the heat pump working fluid discharged from the superheater and the power generation working fluid supplied to the evaporator. By this, the structure further provided with the regenerator which heats the said heat pump working fluid and discharges it to the said evaporator may be sufficient.

  According to such a configuration, since the power generation working fluid preheated by the regenerator is supplied to the evaporator, the flow rate of the heat source fluid supplied from the heat source can be reduced, or a lower temperature heat source fluid can be used. Moreover, the evaporator 12 can be reduced in size.

  In addition, the temperature difference power generation device includes two turbines assembled in series as the turbine, and includes two generators provided corresponding to the two turbines as the generator, The condenser is connected to the turbine on the downstream side so that fluid can flow therethrough, and exchanges heat between the power generation working fluid discharged from the turbine on the upstream side and the power generation working fluid condensed in the condenser, Heat exchange is performed between the heat-exchanging power generation working fluid discharged to the pump, the power generation working fluid discharged from the upstream turbine, and the heat pump working fluid discharged from the superheater. By this, the structure further provided with the reheater which heats the said electric power generation working fluid and discharges | emits to the said turbine of the downstream may be sufficient.

  According to such a configuration, the power generation working fluid reheated by the reheater is supplied to the downstream turbine, so that the power generation efficiency of the downstream power generator can be increased.

  According to the present invention, high power generation efficiency can be realized in a temperature difference power generator.

It is a figure showing typically the temperature difference power generator concerning a first embodiment of the present invention. It is a figure which shows typically the temperature difference power generator which concerns on 2nd embodiment of this invention. It is a figure which shows typically the temperature difference power generator which concerns on 3rd embodiment of this invention. It is a figure which shows typically the temperature difference power generator which concerns on 4th embodiment of this invention. It is a figure which shows typically the temperature difference power generator which concerns on 5th embodiment of this invention. It is a figure which shows typically the temperature difference power generator which concerns on 6th embodiment of this invention. It is a figure which shows typically the temperature difference power generator which concerns on 7th embodiment of this invention.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings as appropriate. Similar parts are denoted by the same reference numerals, and redundant description is omitted. In each figure, the solid line connecting the components is a pipe through which each fluid flows.

<First embodiment>
First, a temperature difference power generator according to a first embodiment of the present invention will be described with reference to FIG. As shown in FIG. 1, a temperature difference power generator 1A according to a first embodiment of the present invention is an apparatus using a Rankine cycle, and includes a pump 11A, an evaporator 12, And a turbine 13A, a generator 14A, a condenser 15, and a tank 16A, and as a component of the heat pump circuit, a compressor 31, a superheater 32, an expansion valve 33, and a heat recovery device 34 .

≪Rankin cycle circuit≫
The pump 11 </ b> A generates a flow of a power generation working fluid (for example, ammonia or pentane which is a low boiling point medium) in the Rankine cycle circuit, and supplies the power generation working fluid to the evaporator 12.

  That is, the downstream end of the pump 11A is connected to the evaporator 12 through a pipe so that fluid can flow.

  The evaporator 12 includes a medium-low temperature (25 to 200 ° C., preferably 70 to 200 ° C.) heat source fluid (for example, exhaust gas discharged from a factory) supplied from a heating heat source H1, and a pump 11A. This is a heat exchanger that heats and vaporizes the power generation working fluid by exchanging heat with the power generation working fluid supplied from. After heat exchange, the heat source fluid is discharged to the heat recovery unit 34, and the vaporized power generation working fluid is discharged to the turbine 13A via the superheater 32.

  That is, the evaporator 12 includes a flow path through which the heat source fluid flows and a flow path through which the power generation working fluid flows, and an upstream end of the heat source fluid flow path is connected to the heat source H1 via a pipe. The downstream end of the flow path for the heat source fluid is connected to the heat recovery unit 34 via a pipe so that the fluid can flow. The upstream end of the flow path for the power generation working fluid is connected to the pump 11A through a pipe so that the fluid can flow, and the downstream end of the flow path for the power generation working fluid is connected via the pipe. It is connected to the superheater 32 so that fluid can flow.

  The turbine 13 </ b> A is a wing-like body that is rotationally driven by the power generation working fluid (vaporized) discharged from the evaporator 12. The power generation working fluid that rotationally drives the turbine 13 </ b> A is discharged to the condenser 15.

  That is, the upstream end of the turbine 13A is connected to the superheater 32 through a pipe so that fluid can flow, and the downstream end of the turbine 13A is connected to the condenser 15 through a pipe so that fluid can flow. Has been.

  The generator 14A is connected to the turbine 13A and is a device that generates power by rotating the turbine.

  The condenser 15 exchanges heat between the power generation working fluid discharged from the turbine 13A and the cooling fluid (for example, seawater, cooling tower water, etc.) supplied from the cooling heat source H2, thereby generating power generation working fluid. It is a heat exchanger that cools and condenses. After the heat exchange, the power generation working fluid is discharged to the tank 16A.

  That is, the condenser 15 includes a flow path through which the cooling fluid flows and a flow path through which the power generation working fluid flows, and an upstream end of the cooling fluid flow path is connected via a pipe. It is connected to the heat source H2 so that fluid can flow, and the downstream end of the cooling fluid flow path is connected to an external device via a pipe so that fluid can flow. Further, the upstream end of the flow path for power generation working fluid is connected to the turbine 13A through a pipe so that fluid can flow, and the downstream end of the flow path for power generation working fluid is connected via a pipe. It is connected to the tank 16A so that fluid can flow therethrough.

  In the tank 16A, the power generation working fluid discharged from the condenser 15 is temporarily stored. The power generation working fluid in the tank 16 </ b> A is pumped out by driving the pump 11 </ b> A and supplied to the evaporator 12 again.

  That is, the upstream end of the tank 16A is connected to the condenser 15 via a pipe so that fluid can flow, and the downstream end of the tank 16A is connected to the pump 11A via a pipe so that fluid can flow. ing.

≪Heat pump circuit≫
The compressor 31 generates a flow of a heat pump working fluid (for example, ammonia, carbon dioxide, etc.) in the heat pump circuit, compresses the heat pump working fluid, and has a higher temperature than the power generation working fluid vaporized by the evaporator 12. To supply to the superheater 32.

  That is, the downstream end of the compressor 31 is connected to the superheater 32 through a pipe so that fluid can flow.

  The superheater 32 exchanges heat between the heat pump working fluid supplied from the compressor 31 and the power generation working fluid discharged from the evaporator 12, thereby further heating the power generation working fluid vaporized in the evaporator 12. It is an exchanger. After heat exchange, the heat pump working fluid is discharged to the expansion valve 33, and the power generation working fluid is discharged to the turbine 13A.

  That is, the superheater 32 includes a flow path through which the heat pump working fluid flows and a flow path through which the power generation working fluid flows, and the upstream end of the heat pump working fluid flow path is connected via a pipe. It is connected to the compressor 31 so that fluid can flow, and the downstream end of the flow path for the heat pump working fluid is connected to the expansion valve 33 via a pipe so that fluid can flow. Further, the upstream end of the flow path for power generation working fluid is connected to the evaporator 12 through a pipe so that fluid can flow, and the downstream end of the flow path for power generation working fluid is connected via a pipe. The turbine 13A is connected to be able to flow fluid.

  The expansion valve 33 is a valve that decompresses and expands (increases the volume) the heat pump working fluid discharged from the superheater 32. After expansion, the heat pump working fluid is discharged to the heat recovery unit 34.

  That is, the upstream end of the expansion valve 33 is connected to the superheater 32 via a pipe so that fluid can flow, and the downstream end of the expansion valve 33 is fluidly connected to the heat recovery unit 34 via the pipe. Connected as possible.

  The heat recovery unit 34 heat-exchanges the heat source fluid discharged from the evaporator 12 and the heat pump working fluid discharged from the expansion valve 33, thereby heating the heat pump working fluid and cooling the heat source fluid. It is a vessel. After heat exchange, the heat pump working fluid is discharged to the compressor 31 and the heat source fluid is discharged to the outside.

  That is, the heat recovery device 34 includes a flow path through which the heat source fluid flows and a flow path through which the heat pump working fluid flows, and the upstream end of the heat source fluid flow path evaporates through the pipe. The downstream end of the flow path for the heat source fluid is connected to an external device through a pipe so that the fluid can flow. The upstream end of the heat pump working fluid channel is connected to the expansion valve 33 via a pipe so that fluid can flow therethrough, and the downstream end of the heat pump working fluid channel is connected to the pipe via the pipe. The compressor 31 is connected so that fluid can flow.

  In the temperature difference power generator 1A according to the first embodiment of the present invention, the heat source fluid supplied from the heat source H1 flows in the order of the evaporator 12 → the heat recovery unit 34 and is discharged to the outside. Further, the cooling fluid supplied from the heat source H2 flows through the condenser 15 and is discharged to the outside. The power generation working fluid circulates in the Rankine cycle circuit in the order of pump 11A → evaporator 12 → superheater 32 → turbine 13A → condenser 15 → tank 16A → pump 11A →. The heat pump working fluid circulates in the heat pump circuit in the order of the compressor 31 → the superheater 32 → the expansion valve 33 → the heat recovery device 34 → the compressor 31 →.

  When the compression efficiency of the compressor 31 is 70% and the power generation efficiency of the turbine 13A and the generator 14A is 10%, the coefficient of performance of the heat pump circuit is 14.3 (= 1 ÷ 0.7 ÷ 0.1) or more. In this case, by setting the temperature of the heat pump working fluid supplied to the superheater 32 to 41 ° C. and the temperature of the heat pump working fluid discharged from the superheater 32 to 20 ° C., the temperature difference power generator 1A can be activated.

The temperature difference power generator 1A according to the first embodiment of the present invention uses ammonia as a power generation working fluid and ammonia as a heat pump working fluid, and the temperature of the heat source fluid supplied to the evaporator 12 is 85.0. ℃, the temperature of the heat pump working fluid supplied to the superheater 32 is 110.0 ℃, the temperature of the heat pump working fluid discharged from the superheater 32 is 80.0 ℃, the temperature of the power generation working fluid supplied to the superheater 32 Is 55.0 ° C., and the temperature of the power generation working fluid discharged from the superheater 32 is 105.0 ° C. (the power generation efficiency of the power generation apparatus using the conventional Rankine cycle having no heat pump circuit is 100. When converted to 0), the power generation efficiency of 203.0 at the maximum can be obtained by subtracting the power used in the compressor 31).
Further, the temperature difference power generator 1A according to the first embodiment of the present invention uses ammonia as a power generation working fluid and ammonia as a heat pump working fluid, and sets the temperature of the heat source fluid supplied to the evaporator 12 to 85.0. ° C, the temperature of the heat pump working fluid supplied to the superheater 32 is 120.0 ° C, the temperature of the heat pump working fluid discharged from the superheater 32 is 82.6 ° C, and the temperature of the power generation working fluid supplied to the superheater 32 Is 55.0 ° C. and the temperature of the power generation working fluid discharged from the superheater 32 is 115.0 ° C. (the power generation efficiency of the power generation apparatus using the conventional Rankine cycle not having the heat pump circuit is 100. When converted to 0), the power generation efficiency of 230.9 at maximum can be obtained by subtracting the power used in the compressor 31).

  The temperature difference power generation device 1A according to the first embodiment of the present invention recovers heat that could not be given to the power generation working fluid by the evaporator 12 to the heat pump working fluid by the heat recovery unit 34, and Since it is given to the power generation working fluid, the enthalpy of the power generation working fluid at the inlet of the turbine 13A can be increased and the power generation efficiency can be increased.

<Second Embodiment>
Subsequently, a temperature difference power generation device according to a second embodiment of the present invention will be described with reference to FIG. 2 with a focus on differences from the temperature difference power generation device 1A according to the first embodiment. As shown in FIG. 2, the temperature difference power generation device 1B according to the second embodiment of the present invention is a device using a Rankine cycle, and further includes a regenerator 35 as a component of the heat pump circuit.

  The regenerator 35 is a heat exchanger that heats the power generation working fluid by exchanging heat between the power generation working fluid discharged from the pump 11 </ b> A and the heat pump working fluid discharged from the superheater 32. After the heat exchange, the power generation working fluid is discharged to the evaporator 12, and the heat pump working fluid is discharged to the expansion valve 33.

  That is, the regenerator 35 includes a flow path through which the power generation working fluid flows and a flow path through which the heat pump working fluid flows, and the upstream end of the flow path for the power generation working fluid is connected via a pipe. The fluid is connected to the pump 11A so that fluid can flow, and the downstream end of the flow path for the power generation working fluid is connected to the evaporator 12 via a pipe so that fluid can flow. The upstream end of the heat pump working fluid channel is connected to the superheater 32 through a pipe so that the fluid can flow therethrough, and the downstream end of the heat pump working fluid channel is connected to the pipe via the pipe. The expansion valve 33 is connected to be able to flow fluid.

  In the temperature difference power generator 1B according to the second embodiment of the present invention, the heat source fluid supplied from the heat source H1 flows in the order of the evaporator 12 → the heat recovery unit 34 and is discharged to the outside. Further, the cooling fluid supplied from the heat source H2 flows through the condenser 15 and is discharged to the outside. The power generation working fluid circulates in the Rankine cycle circuit in the order of pump 11A → regenerator 35 → evaporator 12 → superheater 32 → turbine 13A → condenser 15 → tank 16A → pump 11A →. The heat pump working fluid circulates in the heat pump circuit in the order of the compressor 31 → the superheater 32 → the regenerator 35 → the expansion valve 33 → the heat recovery device 34 → the compressor 31 →.

The temperature difference power generator 1B according to the second embodiment of the present invention uses ammonia as a power generation working fluid and ammonia as a heat pump working fluid, and the temperature of the heat source fluid supplied to the evaporator 12 is 85.0. ℃, the temperature of the heat pump working fluid supplied to the superheater 32 is 110.0 ℃, the temperature of the heat pump working fluid discharged from the superheater 32 is 80.0 ℃, the temperature of the power generation working fluid supplied to the superheater 32 Is 75.0 ° C., and the temperature of the power generation working fluid discharged from the superheater 32 is 105.0 ° C. (assuming that the power generation efficiency of a power generator using a conventional Rankine cycle not having a heat pump circuit is 100) When converted, the power generation efficiency of 203.0 at the maximum can be obtained by subtracting the power used in the compressor 31).
Moreover, the temperature difference power generation device 1B according to the second embodiment of the present invention uses ammonia as the power generation working fluid and ammonia as the heat pump working fluid, and sets the temperature of the heat source fluid supplied to the evaporator 12 to 85.0. ° C, the temperature of the heat pump working fluid supplied to the superheater 32 is 120.0 ° C, the temperature of the heat pump working fluid discharged from the superheater 32 is 82.6 ° C, and the temperature of the power generation working fluid supplied to the superheater 32 Is 55.0 ° C. and the temperature of the power generation working fluid discharged from the superheater 32 is 115.0 ° C. (the power generation efficiency of the power generation apparatus using the conventional Rankine cycle not having the heat pump circuit is 100. When converted to 0), the power generation efficiency of 230.7 at the maximum can be obtained by subtracting the power used in the compressor 31).

  Since the temperature difference power generation device 1B according to the second embodiment of the present invention supplies the power generation working fluid preheated by the regenerator 35 to the evaporator 12, the flow rate of the heat source fluid supplied from the heat source H1 is reduced. Or a lower temperature heat source fluid can be used. Moreover, the evaporator 12 can be reduced in size.

<Third embodiment>
Subsequently, a temperature difference power generation device according to a third embodiment of the present invention will be described with reference to FIG. 3 with a focus on differences from the temperature difference power generation device 1A according to the first embodiment. As shown in FIG. 3, the temperature difference power generation device 1C according to the third embodiment of the present invention is a device using a carina cycle, and includes a gas-liquid separator 17 and a regeneration unit as components of the carina cycle circuit. The container 18, the pressure reducing valve 19, and the absorber 20 are further provided. That is, the Carina cycle circuit is obtained by adding these components to the Rankine cycle circuit.

  The gas-liquid separator 17 separates the power generation working fluid discharged from the evaporator 12 into a gas and a liquid. After separation, the gas (power generation working fluid) is discharged to the superheater 32, and the liquid (power generation working fluid) is discharged to the regenerator 18.

  That is, the upstream end of the gas-liquid separator 17 is connected to the evaporator 12 via a pipe so that fluid can flow, and the downstream end of the gas-liquid separator 17 is connected to the superheater 32 via a pipe. And it is connected to the regenerator 18 so that fluid can flow.

  The regenerator 18 is a heat exchanger that heats the power generation working fluid by exchanging heat between the power generation working fluid discharged from the pump 11A and the liquid (power generation working fluid) discharged from the gas-liquid separator 17. is there. After heat exchange, the power generation working fluid is discharged to the evaporator 12, and the liquid (power generation working fluid) is discharged to the pressure reducing valve 19.

  That is, the regenerator 18 includes a flow path through which a power generation working fluid flows and a flow path through which a liquid (power generation working fluid) flows. An upstream end of the flow path for the power generation working fluid is a pipe. The downstream end of the flow path for the power generation working fluid is connected to the evaporator 12 via a pipe so that the fluid can flow. The upstream end of the liquid (power generation working fluid) flow path is connected to the gas-liquid separator 17 through a pipe so that fluid can flow, and is downstream of the liquid (power generation working fluid) flow path. The side end portion is connected to the pressure reducing valve 19 through a pipe so that fluid can flow.

  The pressure reducing valve 19 is a valve for reducing the pressure of the liquid discharged from the regenerator 18. After decompression, the liquid (power generation working fluid) is discharged to the absorber 20.

  That is, the upstream end of the pressure reducing valve 19 is connected to the regenerator 18 through a pipe so that fluid can flow, and the downstream end of the pressure reducing valve 19 can flow into the absorber 20 through a pipe. It is connected to the.

  The absorber 20 absorbs the liquid (power generation working fluid) discharged from the pressure reducing valve 19 into the power generation working fluid discharged from the turbine 13A. After absorption, the power generation working fluid is discharged to the condenser 15.

  That is, the upstream end of the absorber 20 is connected to the turbine 13A and the pressure reducing valve 19 via a pipe so that fluid can flow, and the downstream end of the absorber 20 is connected to the condenser 15 via a pipe. Connected to allow fluid flow.

  In the temperature difference power generator 1C according to the third embodiment of the present invention, the heat source fluid supplied from the heat source H1 flows in the order of the evaporator 12 → the heat recovery device 34 and is discharged to the outside. Further, the cooling fluid supplied from the heat source H2 flows through the condenser 15 and is discharged to the outside. The power generation working fluid is in the order of pump 11A → regenerator 18 → evaporator 12 → gas-liquid separator 17 → superheater 32 → turbine 13A → absorber 20 → condenser 15 → tank 16A → pump 11A →. Or, the carina cycle circuit in the order of the pump 11A → the regenerator 18 → the evaporator 12 → the gas-liquid separator 17 → the regenerator 18 → the pressure reducing valve 19 → the absorber 20 → the condenser 15 → the tank 16A → the pump 11A →. Circulate inside. The heat pump working fluid circulates in the heat pump circuit in the order of the compressor 31 → the superheater 32 → the expansion valve 33 → the heat recovery device 34 → the compressor 31 →.

The temperature difference power generator 1C according to the third embodiment of the present invention uses a mixture of ammonia and water as a power generation working fluid and also uses ammonia as a heat pump working fluid, and the heat source fluid supplied to the evaporator 12 The temperature is 28.0 ° C., the temperature of the heat pump working fluid supplied to the superheater 32 is 60.0 ° C., the temperature of the heat pump working fluid discharged from the superheater 32 is 40.0 ° C., and the superheater 32 is supplied. When the temperature of the power generation working fluid is 25.6 ° C. and the temperature of the power generation working fluid discharged from the superheater 32 is 55.0 ° C. (of a power generation device using a conventional carina cycle that does not have a heat pump circuit) When the power generation efficiency is converted to 100.0, the power generation efficiency of 176.0 at the maximum can be obtained by subtracting the power used in the compressor 31).
In addition, the temperature difference power generation device 1C according to the third embodiment of the present invention uses a mixture of ammonia and water as a power generation working fluid and uses ammonia as a heat pump working fluid, and the heat source fluid supplied to the evaporator 12 The temperature is 28.0 ° C., the temperature of the heat pump working fluid supplied to the superheater 32 is 70 ° C., the temperature of the heat pump working fluid discharged from the superheater 32 is 40.0 ° C., and the power generation operation supplied to the superheater 32 When the temperature of the fluid is 25.6 ° C. and the temperature of the power generation working fluid discharged from the superheater 32 is 65.0 ° C. (the power generation efficiency of the power generation apparatus using a conventional carina cycle not having a heat pump circuit) The power generation efficiency of 194.1 at the maximum can be obtained by subtracting the power used in the compressor 31).

  Since the temperature difference power generation device 1C according to the third embodiment of the present invention supplies the power generation working fluid preheated by the regenerator 18 to the evaporator 12, the flow rate of the heat source fluid supplied from the heat source H1 is reduced. Or a lower temperature heat source fluid can be used.

<Fourth embodiment>
Next, a temperature difference power generation device according to a fourth embodiment of the present invention will be described with reference to FIG. 4 with a focus on differences from the temperature difference power generation device 1C according to the third embodiment. As shown in FIG. 4, the temperature difference power generation device 1D according to the fourth embodiment of the present invention is a device using a carina cycle, and further includes a regenerator 35 as a component of the heat pump circuit.

  The regenerator 35 is a heat exchanger that heats the power generation working fluid by exchanging heat between the power generation working fluid discharged from the regenerator 18 and the heat pump working fluid discharged from the superheater 32. After the heat exchange, the power generation working fluid is discharged to the evaporator 12, and the heat pump working fluid is discharged to the expansion valve 33.

  That is, the regenerator 35 includes a flow path through which the power generation working fluid flows and a flow path through which the heat pump working fluid flows, and the upstream end of the flow path for the power generation working fluid is connected via a pipe. It is connected to the regenerator 18 so that fluid can flow, and the downstream end of the flow path for the power generation working fluid is connected to the evaporator 12 via a pipe so that fluid can flow. The upstream end of the heat pump working fluid channel is connected to the superheater 32 through a pipe so that the fluid can flow therethrough, and the downstream end of the heat pump working fluid channel is connected to the pipe via the pipe. The expansion valve 33 is connected to be able to flow fluid.

  In the temperature difference power generator 1D according to the fourth embodiment of the present invention, the heat source fluid supplied from the heat source H1 flows in the order of the evaporator 12 → the heat recovery unit 34 and is discharged to the outside. Further, the cooling fluid supplied from the heat source H2 flows through the condenser 15 and is discharged to the outside. The power generation working fluid is pump 11A → regenerator 18 → regenerator 35 → evaporator 12 → gas-liquid separator 17 → superheater 32 → turbine 13A → absorber 20 → condenser 15 → tank 16A → pump 11A → In this order, or pump 11A → regenerator 18 → regenerator 35 → evaporator 12 → gas-liquid separator 17 → regenerator 18 → reducing valve 19 → absorber 20 → condenser 15 → tank 16A → pump 11A → It circulates in the carina cycle circuit in the order of. The heat pump working fluid circulates in the heat pump circuit in the order of the compressor 31 → the superheater 32 → the regenerator 35 → the expansion valve 33 → the heat recovery device 34 → the compressor 31 →.

The temperature difference power generator 1D according to the fourth embodiment of the present invention uses a mixture of ammonia and water as a power generation working fluid and also uses ammonia as a heat pump working fluid, and the heat source fluid supplied to the evaporator 12 The temperature is 28.0 ° C., the temperature of the heat pump working fluid supplied to the superheater 32 is 60.0 ° C., the temperature of the heat pump working fluid discharged from the superheater 32 is 40.0 ° C., and the superheater 32 is supplied. When the temperature of the power generation working fluid is 25.6 ° C. and the temperature of the power generation working fluid discharged from the superheater 32 is 55.0 ° C. (of a power generation device using a conventional carina cycle that does not have a heat pump circuit) When the power generation efficiency is converted to 100.0, a maximum power generation efficiency of 178.2 can be obtained even if the power used in the compressor 31 is subtracted.
In addition, the temperature difference power generator 1D according to the fourth embodiment of the present invention uses a mixture of ammonia and water as a power generation working fluid and uses ammonia as a heat pump working fluid, and the heat source fluid supplied to the evaporator 12 The temperature is 28.0 ° C., the temperature of the heat pump working fluid supplied to the superheater 32 is 70 ° C., the temperature of the heat pump working fluid discharged from the superheater 32 is 40.0 ° C., and the power generation operation supplied to the superheater 32 When the temperature of the fluid is 25.6 ° C. and the temperature of the power generation working fluid discharged from the superheater 32 is 65.0 ° C. (the power generation efficiency of the power generation apparatus using a conventional carina cycle not having a heat pump circuit) The power generation efficiency of 196.2 at the maximum can be obtained by subtracting the power used in the compressor 31).

  Since the temperature difference power generation device 1D according to the fourth embodiment of the present invention supplies the power generation working fluid preheated by the regenerator 35 to the evaporator 12, the flow rate of the heat source fluid supplied from the heat source H1 is reduced. Or a lower temperature heat source fluid can be used. Moreover, the evaporator 12 can be reduced in size.

<Fifth embodiment>
Next, a temperature difference power generation device according to a fifth embodiment of the present invention will be described with reference to FIG. 5 with a focus on differences from the temperature difference power generation device 1C according to the third embodiment. As shown in FIG. 5, the temperature difference power generation device 1E according to the fifth embodiment of the present invention is a device that uses a Wafer cycle, and includes a turbine 13E, a generator 14E, and the components of the Wafer cycle circuit. , A tank 16E, a pump 11E, and a heater 21 are further provided. In other words, the Uehara cycle circuit is obtained by adding these components to the carina cycle circuit.

  The turbine 13E is provided on the upstream side of the turbine 13A and is a wing-like body that is rotationally driven by the power generation working fluid discharged from the superheater 32. A part of the power generation working fluid that rotationally drives the turbine 13 </ b> E is discharged to the downstream turbine 13 </ b> A, and the other part is discharged to the heater 21.

  That is, the upstream end of the turbine 13E is connected to the superheater 32 via a pipe so that fluid can flow, and the downstream end of the turbine 13E flows to the turbine 13A and the heater 21 via the pipe. Connected as possible.

  The generator 14E is connected to the turbine 13E and is a device that generates power by rotating the turbine.

  The power generation working fluid discharged from the condenser 15 is temporarily stored in the tank 16E.

  That is, the upstream end of the tank 16E is connected to the condenser 15 via a pipe so that fluid can flow, and the downstream end of the tank 16E is connected to the pump 11E via a pipe so that fluid can flow. ing.

  The pump 11E generates a flow of the power generation working fluid in the Uehara cycle circuit together with the pump 11A. The pump 11E pumps the power generation working fluid in the tank 16E and supplies it to the heater 21.

  That is, the upstream end of the pump 11E is connected to the tank 16E via a pipe so that fluid can flow, and the downstream end of the pump 11E is connected to the heater 21 via a pipe so that fluid can flow. ing.

  The heater 21 is a heat exchanger that reduces a temperature difference between the power generation working fluid discharged from the turbine 13E and the power generation working fluid discharged from the pump 16E. After the heat exchange, both of these power generation working fluids are discharged to the tank 16A.

  That is, the heater 21 includes a flow path through which the power generation working fluid discharged from the turbine 13E flows and a flow path through which the power generation working fluid discharged from the pump 11E flows, and is discharged from the turbine 13E. The upstream end of the flow path for the power generation working fluid is connected to the turbine 13E via a pipe so that the fluid can flow, and the downstream end of the flow path for the power generation working fluid discharged from the turbine 13E is It is connected to the tank 16A through a pipe so that fluid can flow. Further, the upstream end of the flow path for the power generation working fluid discharged from the pump 11E is connected to the pump 11E through a pipe so that the fluid can flow, and the flow for the power generation working fluid discharged from the pump 11E. The downstream end of the path is connected to the tank 16A through a pipe so that fluid can flow.

  In the temperature difference power generator 1E according to the fifth embodiment of the present invention, the heat source fluid supplied from the heat source H1 flows in the order of the evaporator 12 → the heat recovery unit 34 and is discharged to the outside. Further, the cooling fluid supplied from the heat source H2 flows through the condenser 15 and is discharged to the outside. The power generation working fluid is pump 11A → regenerator 18 → evaporator 12 → gas-liquid separator 17 → superheater 32 → turbine 13E → turbine 13A → absorber 20 → condenser 15 → tank 16E → pump 11E → heater. 21 → tank 16A → pump 11A →..., Pump 11A → regenerator 18 → evaporator 12 → gas-liquid separator 17 → superheater 32 → turbine 13E → heater 21 → tank 16A → pump 11A → Or in the order of pump 11A → regenerator 18 → evaporator 12 → gas / liquid separator 17 → regenerator 18 → reducing valve 19 → absorber 20 → condenser 15 → tank 16E → pump 11E → heater 21 → tank It circulates in the wafer cycle circuit in the order of 16A → pump 11A →. The heat pump working fluid circulates in the heat pump circuit in the order of the compressor 31 → the superheater 32 → the expansion valve 33 → the heat recovery device 34 → the compressor 31 →.

  The temperature difference power generator 1E according to the fifth embodiment of the present invention is provided with two sets of turbines and generators (upstream turbine 13E and generator 14E, downstream turbine 13A and generator 14A). Efficiency can be further increased.

<Sixth embodiment>
Subsequently, a temperature difference power generation device according to a sixth embodiment of the present invention will be described with reference to FIG. 6 with a focus on differences from the temperature difference power generation device 1E according to the fifth embodiment. As shown in FIG. 6, the temperature difference power generation device 1F according to the sixth embodiment of the present invention is a device that uses a Uehara cycle, and further includes a regenerator 35 as a component of the heat pump circuit.

  The regenerator 35 is a heat exchanger that heats the power generation working fluid by exchanging heat between the power generation working fluid discharged from the regenerator 18 and the heat pump working fluid discharged from the superheater 32. After the heat exchange, the power generation working fluid is discharged to the evaporator 12, and the heat pump working fluid is discharged to the expansion valve 33.

  That is, the regenerator 35 includes a flow path through which the power generation working fluid flows and a flow path through which the heat pump working fluid flows, and the upstream end of the flow path for the power generation working fluid is connected via a pipe. It is connected to the regenerator 18 so that fluid can flow, and the downstream end of the flow path for the power generation working fluid is connected to the evaporator 12 via a pipe so that fluid can flow. The upstream end of the heat pump working fluid channel is connected to the superheater 32 through a pipe so that the fluid can flow therethrough, and the downstream end of the heat pump working fluid channel is connected to the pipe via the pipe. The expansion valve 33 is connected to be able to flow fluid.

  In the temperature difference power generator 1F according to the sixth embodiment of the present invention, the heat source fluid supplied from the heat source H1 flows in the order of the evaporator 12 → the heat recovery device 34 and is discharged to the outside. Further, the cooling fluid supplied from the heat source H2 flows through the condenser 15 and is discharged to the outside. The power generation working fluid is pump 11A → regenerator 18 → regenerator 35 → evaporator 12 → gas-liquid separator 17 → superheater 32 → turbine 13E → turbine 13A → absorber 20 → condenser 15 → tank 16E → pump. 11E → heater 21 → tank 16A → pump 11A →..., Pump 11A → regenerator 18 → regenerator 35 → evaporator 12 → gas-liquid separator 17 → superheater 32 → turbine 13E → heater 21 → Tank 16A → Pump 11A →... Or Pump 11A → Regenerator 18 → Regenerator 35 → Evaporator 12 → Gas-liquid separator 17 → Regenerator 18 → Pressure reducing valve 19 → Absorber 20 → Condenser 15 → Tank 16E → Pump 11E → Heater 21 → Tank 16A → Pump 11A →... The heat pump working fluid circulates in the heat pump circuit in the order of the compressor 31 → the superheater 32 → the regenerator 35 → the expansion valve 33 → the heat recovery device 34 → the compressor 31 →.

  Since the temperature difference power generation device 1F according to the sixth embodiment of the present invention supplies the power generation working fluid preheated by the regenerator 35 to the evaporator 12, the flow rate of the heat source fluid supplied from the heat source H1 is reduced. Or a lower temperature heat source fluid can be used. Moreover, the evaporator 12 can be reduced in size.

<Seventh embodiment>
Subsequently, a temperature difference power generation device according to a seventh embodiment of the present invention will be described with reference to FIG. 7, focusing on differences from the temperature difference power generation device 1E according to the fifth embodiment. As shown in FIG. 7, the temperature difference power generation device 1G according to the seventh embodiment of the present invention is a device that uses a Uehara cycle, and further includes a reheater 36 as a component of the heat pump circuit.

  The reheater 36 is a heat exchanger that reheats the power generation working fluid by exchanging heat between the power generation working fluid discharged from the upstream turbine 13E and the heat pump working fluid discharged from the superheater 32. is there. After the heat exchange, the power generation working fluid is discharged to the turbine 14E, and the heat pump working fluid is discharged to the expansion valve 33.

  That is, the reheater 36 includes a flow path through which the power generation working fluid discharged from the turbine 13E flows, and a flow path through which the heat pump working fluid discharged from the superheater 32 flows. The upstream end of the flow path is connected to the turbine 13E via a pipe so that fluid can flow, and the downstream end of the power generation working fluid flow path can flow to the turbine 13A via a pipe. It is connected to the. The upstream end of the heat pump working fluid channel is connected to the superheater 32 through a pipe so that the fluid can flow therethrough, and the downstream end of the heat pump working fluid channel is connected to the pipe via the pipe. The expansion valve 33 is connected to be able to flow fluid.

  In the temperature difference power generator 1G according to the seventh embodiment of the present invention, the heat source fluid supplied from the heat source H1 flows in the order of the evaporator 12 → the heat recovery unit 34 and is discharged to the outside. Further, the cooling fluid supplied from the heat source H2 flows through the condenser 15 and is discharged to the outside. The power generation working fluid is pump 11A → regenerator 18 → evaporator 12 → gas / liquid separator 17 → superheater 32 → turbine 13E → reheater 36 → turbine 13A → absorber 20 → condenser 15 → tank 16E → Pump 11E → heater 21 → tank 16A → pump 11A →... Pump 11A → regenerator 18 → evaporator 12 → gas-liquid separator 17 → superheater 32 → turbine 13E → heater 21 → tank 16A → Pump 11A → ... in this order, or pump 11A → regenerator 18 → evaporator 12 → gas-liquid separator 17 → regenerator 18 → reducing valve 19 → absorber 20 → condenser 15 → tank 16E → pump 11E → It circulates in the wafer cycle circuit in the order of the heater 21 → tank 16A → pump 11A →. The heat pump working fluid circulates in the heat pump circuit in the order of the compressor 31 → the superheater 32 → the reheater 36 → the expansion valve 33 → the heat recovery device 34 → the compressor 31 →.

  Since the temperature difference power generation device 1F according to the seventh embodiment of the present invention supplies the power generation working fluid reheated by the reheater 36 to the downstream turbine 13A, the power generation efficiency in the downstream generator 14A is increased. Can be increased.

  As mentioned above, although embodiment of this invention was described, this invention is not limited to the said embodiment, A design change is possible suitably in the range which does not deviate from the summary of this invention. For example, the reheater 36 in the temperature difference power generation device 1G of the seventh embodiment can be added to the temperature difference power generation device 1F of the sixth embodiment. Moreover, the temperature difference power generators 1A to 1G use not only power generation using exhaust gas discharged from a factory, warm drainage as a heat source fluid, but also relatively warm hot sea water in the ocean surface as a heat source fluid and in the deep ocean. The present invention can also be applied to ocean temperature differential power generation using relatively low-temperature cold seawater as a cooling fluid, geothermal power generation using geothermal heat, steam, or the like as a heat source fluid.

1A, 1B, 1C, 1D, 1E, 1F, 1G Temperature difference generator 11A, 11E Pump 12 Evaporator 13A, 13E Turbine 14A, 14E Generator 15 Condenser 16A, 16E Tank 17 Gas-liquid separator 18 Regenerator 19 Depressurization Valve 20 Absorber 21 Heater 31 Compressor 32 Superheater 33 Expansion valve 34 Heat recovery device 35 Regenerator 36 Reheater H1, H2 Heat source

Claims (3)

An evaporator that vaporizes the power generation working fluid by exchanging heat between the heat source fluid supplied from the heat source and the power generation working fluid;
A pump for supplying the power generation working fluid to the evaporator;
A turbine driven by the power generation working fluid vaporized in the evaporator;
A generator for generating electricity by driving the turbine;
A condenser for condensing the power generation working fluid discharged from the turbine and discharging it to the pump;
A temperature difference power generation device comprising:
A compressor for compressing the heat pump working fluid;
The heat generating working fluid is superheated by exchanging heat between the heat pump working fluid provided between the evaporator and the turbine and compressed by the compressor and the power generating working fluid vaporized by the evaporator. A superheater discharged to the turbine,
An expansion valve for expanding the heat pump working fluid discharged from the superheater;
A heat recovery unit that heats and discharges the heat pump working fluid to the compressor by exchanging heat between the heat pump working fluid discharged from the expansion valve and the heat source fluid discharged from the evaporator;
A temperature difference power generation device comprising: The heat pump working fluid is heated by exchanging heat between the heat pump working fluid provided between the pump and the evaporator and discharged from the superheater and the power generation working fluid supplied to the evaporator. The temperature difference power generator according to claim 1, further comprising a regenerator that discharges to the evaporator. The turbine includes two turbines assembled in series, and the generator includes two generators provided corresponding to the two turbines, respectively.
The condenser is connected to the turbine on the downstream side so that fluid can flow therethrough,
A heater for exchanging heat between the power generation working fluid discharged from the turbine on the upstream side and the power generation working fluid condensed by the condenser and discharging the heat-exchanged power generation working fluid to the pump; ,
By exchanging heat between the power generation working fluid discharged from the upstream turbine and the heat pump working fluid discharged from the superheater, the power generation working fluid is heated and discharged to the downstream turbine. A heater,
The temperature difference power generator according to claim 1, further comprising:

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